Fluid pressure device



March 9, 194 c. M. KENDRICK ET AL 2,313,245

FLUID PRES SURE DEVICE Filed May 51, 1941' a Sheets-Sheet i 24 3 .9/ 0 93 72 3 I f 7/ I u AT ORNEYS March 9, 1943'. c. M. KENDRIC'K ET AL 3 -33 FLUID PRESSURE DEVICE Filed May 51, 1941 e Sheets-She't 2 C/Q'A/WE s JPPE A/bkIcK March 9, 1943.

- FLUID PRESSURE DEVICE Filed May 31, 1941.

6 Sheets-Sheet 5 AT ORNEYS c. M. KENDRICK EIAL 7 ,246 I M i w Mada 9i, 1Q43.

FLU-ID PRES SURE DEVICE -Filed May 31, 1941 6 Sheets-Sheet 4 ATTORNEYS c. MpKENDlICK ETAL 2,313,246 I March 9, 1943.

c. M. KENDRICK ET AL FLUID PRESSURE DEVICE Filed May 31, 1941 6 Shets-Sheet 5 AT ORNEYS March. 9, 1943.

c. M. KENDRICK ETAL FLUID PRESSURE DEYIGE -Filed May 31, 1941 6 Sheets-Sheet 6 Patented Mar. 9, '1943 FLUID PRESSURE DEVICE Charles M. Kendrick and Ivan A. Kazine, New York, N. Y., assig'nors to Manly Corporation, Washington, D. 0., a corporation of Delaware Application May 31', 1941, Serial No. 395,950

(01. 103-120) This invention relates to vane type rotary 31 Claims.

fluid pressure devices such, for, example, as

pumps or fluid motors, the volumetric capacity or output per revolution of which can be regulated or varied, and it relates, more particularly, to improvements in that portion of the fluid pressure device by means of which suchvariation of capacity or output is obtained.

The widest present use for fluid pressure devices of this general class is as hydraulic devices, that is, devices for handling or whose motive fluid is a liquid, such, for example, as oil, and the fluid pressure device of the present invention will be described in connection with such use. It will be understood, however, that the invention is applicable to fluid pressure devices operating with elastic fluids.

Fluid pressure devices of the type under consideration include a rotor provided with vanes which are movable inwardly and outwardly in a general radial direction and arranged to rotate within a chamber having side walls which closely fit the sides of the rotor and the side edges of the vanes. A vane track, which surrounds the radially outer ends of the vanes and controls their inward and outward movement, comprises one or more pairs of abutments and interconnecting track elements. pair is preferably arranged in fixed position ad- Jacent the circumferential surface of the rotor and the other abutment of each pair is adapted to be radially adjusted with respect to said circumferential rotor surface. With this preferred arrangement the work of the fluid pressure device is done while the vanes move across an are on the working or movable abutment of each pair, termed the working or pumping are, which, when the device is at other than zero stroke, is spaced radially from the circumferential surface of the rotor, forming a working or fluid transfer chamber. The circulated fluid is received on one circumferential end of this working chamber or pumping arc and discharged on the other. I

The volumetric capacity or output per revolution of the fluid pressure device is regulated or varied by radially adjustingv the working or movable abutment of each pair with respect .to the surface of the rotor. The interconnecting track element or elements serve to guide and convey the outer ends of the vanes from one abutment to another in all positions of the. movable abutment, permitting radial adjustment of the movable abutment without changing the radial posi: tion of the other abutment of each pair.

One abutment of each Our co-pending application Serial Number 263,649, filed March 23, 1939, relates to such a fluid pressure device and, while the construction therein disclosed has been found to be' successful, the present invention concerns certain improvements which further facilitate manufacture and which increase the scope of usefulness of the device while retaining the advantages of our previous construction. The general object of the present invention, therefore, is to provide an improved variable-capacity vane type fluid pressure device of this character. Another and important object is to improve the construction and arrangement of the vane track and its associated mechanism by means of which the volumetric capacity per revolution of the rotor of the fluid pressure device is determined, and regulated and varied, and'by which the inward and outward movements of the varies are controlled.

The fluid pressure device of the present invention difiers importantly from that disclosed in the above-mentioned co-pending application in several respects, one of which is the means and arrangement by which the interconnecting track elements (which are disposedintermediatath fixed and movable abutments and which in the embodiments illustrated are substantiallyrigid) are mounted and by which their movement and position are controlled relative to the track surfaces on the adjacent fixed and movable abutments. For example, in the arrangement of our co-pending application each interconnecting track element is pivotally mounted on its corresponding fixed abutment or other suitable stationary part of the track or casing assembly, whereas in the arrangement of the present in vention' the end of each interconnecting track element adjacent the fixed abutment has an extensible connection with said fixed abutment, the advantages of which will be hereinafter pointed out. The present invention further provides an arrangement in which the intercon necting' track elements have extensible connections with both the adjacent fixed and movable abutments, whereas our former construction provided an extensible connection with the abutment at only one end of the interconnecting track member, that is to say, at the end thereof adjacentthe movable abutment.

The arrangement of the present invention still further provides simple, novel and improved means, housed within the enclosing casing, for conjointly moving the movable abutments of the vane track assembly in order to alter the capacits rotor.

The invention will be understood from consideration of the accompanying drawings which illustrate, by way of example, a number of embodiments of the invention in a pump having two working or pumping chambers, that is to say, in' a so-called double or double-acting pump. It will be understood, however, that the invention is also applicable to other fluid pressure devices such, for example, as fiuid motors and that the fiu id pressure device can be made a single or single acting device having only one working chamber and also that morethan two working chambers may be employed if desired.

In the accompanying drawings:

Fig. 1 is a longitudinal sectional view taken along the lines of Figs. 2 and 3;

Fig. 2 is a vertical view transverse the axis of rotation of the rotor, partially in section, along the line 2-2 of Fig. 1 but with certain of the elements wholly or partially shown in end elevation;

Fig. 3 is also a transverse sectional view but is taken along the line 33 of Fig. 1 looking in a direction opposite to that of Fig. 2 as indicated by the arrows;

Fig. 4 shows an elevation of the inner or rotor face of one of the members, for convenience termed the casing cheek plate;

Fig. 5 is an enlarged perspective view of th elements comprising the improved vane track illustrated in Figs. 1 and 2, with these elements separated from but showing their relation to one another;

Fig. 6 is a perspective view of one of the elements shown in Fig. 5, for convenience termed a movable abutment, drawn to substantially the same scale as that of Fig. 5 but viewed from a different angle;

Fig. 7 is an enlarged fragmentary view, somewhat exaggerated, showing the position of the end of a link member illustrated in Figs. 1, 2 and 5 relative to its corresponding fixed abutment when the movable abutment thereof is adjusted to its full stroke or maximum outward position;

Fig. 8 is a view generallysimilar to Fig. 7 showing the relative positions of the parts when the movable abutment is adjusted to its minimum stroke or extreme inward position; 1

Fig. 9 is a perspective view of the double torsion type spring shown in Figs. 1 and 2;

Fig. 10 is an enlarged perspective view of two of the elements comprising the improved adjusting and control means illustrated in Fig. 2, with the elements separated from but showing their relation to one another;

Fig. 11 is an enlarged perspective view of another of the elements comprising the improved adjusting and control means;

Fig. 12 illustrates a modification which is shown partly in section and partly in schematic arrangement;

Fig. 13 is an enlarged perspective view of, the elements comprising the modified vane track illustrated in Fire-12, with the elements thereof separated from but"showing their relation to one another;

' Fig. 14 is a diagrammatic view showing certain features of construction and arrangement of the modified vane track elements illustrated in Figs. 12 and 13; 7

Figs. 15, 16 and 17 are views corresponding ity of the fluid pressure device per revolution of generally to Figs. 12, 13 and 14 respectively but showing another modification;

Figs. 18 and 19 are views corresponding generally to Figs. 1,2 and 13 but showing a further modification;

Fig. 20 shows an elevation of the inner or rotor face of a modified member, for convenience termed the casing cheek plate, which is employed with the modified vane track elements illustrated in Figs. 18 and 19; and

Figs. 21 and 22 are enlarged fragmentary views showing certain details and features, of construction of the modified arrangement illustrated in Figs. 18 and 19.

Referring first to the embodiment illustrated in Figs. 1 to .11 inclusive of these drawings, the pump includes a casing 10 and an end head or cover H which co-operate to form a cavity for the rotor l5 and associated parts as shown in Figs. 1 and 2. The rotor I5 is provided with a plurality of substantially radial vane slots in each of which is a. vane |1 arranged for movement inward and outward thereof in a substantially radial direction.

The rotor l5 and shaft l8 may be'mounted and the two parts operatively connected with each other in any appropriate way. In the present instance the rotor I5, shaft l8, their mountings and the operative connections therebetween are the same as disclosed in co-pending application filed December 8, 1939', Serial Number 307,- 755. As shown in Fig. 1, the shaft I8 is revolubly supported by a pair of bearing elements I3 and I4 carried by the casing I0 and the rotor I5 is mounted on the end of the shaft i8 which projects into the rotor cavity. For this purpose the end 'of the shaft I8 is formed with axially extending splines l9 (Figs. 1 and 2) and the rotor I5 is formed in its central opening with mating splines l6 (Fig. 2). The arrangement is such that the rotor I5 is freely movable in an axial direction on the shaft splines I9 while permitting a limited tilting or rocking motion of the rotor l5 relative to the shaft H3 in such manner that the cheek plates 26 and 21 to be presently described, determine the axial and angular positions of the rotor on the shaft and the plane of rotation of the rotor as fully explained in capending application Serial Number 307,755 above mentioned.

A substantially annular spacer ring, broadly designated by the numeral 20, surrounds the rotor and vane assembly. The spacer ring 20 is recessed on both its faces and adjacent its central opening to form an inner web portion 2| (Fig. 1) which separates a pair of disk-shaped end plates or cheek plates 26 and 21 respectively {having holes at their centers for the shaft l8 "and whose inner opposing faces form fluid tight fits with the faces 22 of the web portion 2|. The web portion 2| thus separates and axially positions the cheek plates 26 and 21 with respect to the rotor I5 and the arrangement is such that the rotor is permitted toturn freely while its sides and the side edges of the vanes N form substantially fluid-tight running fits with the adjacent faces of the cheek plates 26 and 21. The outer faces of the cheek plates 26 and 21 are adapted to fit snugly against the wall surfaces of the casing Hi and end head M respectively and to form substantially fluid-tight joints with the ports and passages in the casing I0. In order that the cheek plates 26 and 21 may assuredly provide the above-mentioned fluid-tight fits with the wall surfaces of the casing I0 and of the end the two cheek plates 26 and 21 and the web portion 2| exceed the thickness or axial dimension of the outer flange portion 23 of the spacer ring 20 as illustrated in Fig. 1. With this preferred arrangement there is a space between the wall surfaces of the casing l and end'head ll respectively and the faces of the outer flange portion 23 and the substantially fluid-tight fits between the parts above-mentioned'may be readily obtained by tightening the cap screws l2 (Fig. 1) which fasten the end head II to the casing ID. The cheek plate 26 will hereinafter be referred .to as the casing cheek plate" and the cheek plate 21 will be referred to as the end head cheek plate.

The space within the chamber formed by the cheek plates 26 and 21 and which surrounds the rotor I is divided into a plurality of fluid sections, preferably two, each consisting of a working or pumping chamber flanked by an inlet area and an .outlet area. In the embodiment illustrated in Figs. 1-11 inclusive, this space surrounding the rotor is divided into two fluid sections by a pair of diametrically positioned fixed abutments 30 (Fig. 2) which extend inward from the spacer ring 26 and are positioned above and below the rotor l 5 adjacent the vertical centerline thereof. Each fixed abutment 30 is received within an appropriate recess formed in the spacer ring 20 and is held in place by a screw 3|, the arrangement being such that each fixed abutment 30 forms a substantially fluid-tight seal with the bottom of its corresponding recess. Each fixed abutment 30 is of the same thickness as that of the web. 2| of the spacer ring 20 and thus forms a substantially fluid-tight: seal with the faces of the cheek plates 26 and 21. The interior surface of each fixed abutment 30 includes an arcuate track surface 32 (Figs. 2 and 5), termed a sealing arc, preferably concentric with the rotor [5 but not necessarily so, which is adapted to form a substantially fluidtight sliding fit with the ends of the vanes l1 and which has an angular length equal to or slightly greater than the distance between a pair of adjacent vanes H; the sealing arcs 32 are preferably spaced from the rotor l5 so as to provide a small clearance between said sealing arcs 32 and the periphery of the rotor IS, the purpose of which will be hereinafter explained. The fixed abutments 30. thus co-operate with the rotor l5 and vanes I! to form the divisions between the pumps two fluid sections.

The working orpumping chambers of the two fluid sections are formed by means of two diametrically positioned movable abutments 40, acting in conjunction with the rotor and vanes. The abutments 40 are shownin side elevation in Fig. 2 and one is shown in perspective in Figs. 5 and 6.

1 The working or pumping chambers are formed by means of the two diametrically positioned working or pumping arcs 4 l one of ,which is formed on the inner end or surface of each of the-movable abutments 40 with the center line of each arc 4| preferably in line with the horizontal center line of the corresponding abutment 40. Each working or pumping chamber extends in a circumferential direction for a distance equal to the space between two adjacent vanes I! which at any given instant are moving in contact with the corresponding working or pumping arc 4|, The arcs 4| will hereinafter be referred to as the pumping arcs. The size of thepumping chambers, and.

in the spacer ring 20 as shown in Fig. 2; the pres-' ent invention provides simple and improved means (to be later described) by which such movement of the two movable abutments 40 may be conjointly effected, but it will be understood that any other suitable means may be employedfor this purpose.

An important feature of the present invention is the construction and arrangement of the vane track by means of which the outer ends of, the vanes are guided in their in-and-out movement as the rotor revolves. This vane track comprises the inner or vane-contacting surfaces of the fixed abutments 30, the movable abutments and of interconnecting track elements which extend'in a generally circumferential direction between these abutments to guide the vanes as they move from one abutment to another as the rotor revolves. In the present embodiment the interconnecting track elements 'take the form of substantially rigid (that is to say, not readily bendable) links 50 as shown in Figs.'2 and 5,

and these members will hereinafter be termed 'the links, track links, etc.

track links 50 are employed in .each of the two Two Of these fluid sections of the pump of the present embodiment and serve to connect the movable abutment 4!] thereof with the two fixed abutments 30 as shown in Fig. -2 and all four of the links 50 are preferably identical with one another.

The end of each link 50 is forked adjacent its corresponding movable abutment 40, as indicated at 5l in Fig. 5, in order to receive the reduced end portion 42 of the movable abutment. The end of each link 50 adjacent its corresponding fixed abutment 30 is reduced in width to form a tongue 52 (Figs. 5, 7 and 8) which extends into a slot 33 on the adjacent end of saidfixed abutment 30, the slot 33 on each end of each fixed abutment 30 thus providing a pair of arms 34 one of which is disposed on each side of the tongue 52. The side faces of theforked end 5| and of the tongue 52 of the link 50 may have sliding fits with the movable abutments reduced end portion 42) and with the side faces of the arms 34 respectively but a small clearance between these parts is usually preferhence'the volume of fluid delivered per revolution able for convenience in manufacture and assemblyand in order to prevent binding as the parts of the vane track are movedv relative to each other when the output of the pump is altered. Thereduced end portion 42 of the movable abutment 40 extends into the forked end 5| of the 1 .link50 and the tongue 52 extends into the slot 33 in such manner that the vane-contacting surfaces on the link overlap the vane-contacting surfaces of the abutments in all positions of adjustment of the vane track, as will be understood from' Figs. 2, 5, 7 and 8.

Each link is provided with at least 'one pivotal mounting which contributes toward its positioning with.respect to the track surfaces on the fixed and movable abutments and co-ordina'tes its movement with that of the corresponding movable abutment. In the embodiment illus- 52 of each link 50 is supported and positioned-by g a pin 55 which extends through a. suitable hole in the short arm 56 adjacent the end of the tongue 52 and also extends into a slot 35 formed in each arm 34 of the fixed abutments 30, as shown in Figs. 2, 5, '7 and 8.

contour of the vane track, that is to say, of the vane-contacting surfaces of the vane track, particularly at the more critical regions adjacent the fixed abutments where the radial velocity of the vanes is relatively low. For example, with the present arrangement the contour of the vanetrack surfaces may be made such that under the influence of centrifugal force alone the vanes move outward and remain in contact with the track surfaces as said vanes pass through the inlet areas of the pump. This track following action of the vanes under the influence of With this arrangement, each link 50 is moved conformably with the extent and direction of the adjusting movement of its corresponding movable abutment 40 by means of the pivotal t connection between them provided by the pin 53, this movement taking place as said movable abutment 40 is moved inward or outward to alter the output of the pump. As the link 50 moves in unison with the movable abutment 40, the pin 55 moves in the slots 35 and thetongue 52 is thus guided and its position controlled relative to the track surfaces 36 on the arms 34 of the fixed abutment 30. A sliding, extensible connection is thus provided between the fixed abutment 30 and the tongue 52 of the link 50 and the only rocking or tilting of the link 50 about its pivotal mounting on the movable abutment 40 is the amount produced by change in the vertical distance between the pin 55 and the horizontal center line of the pump, this change in vertical distance being determined by the contour of the slots 35. Rocking or tilting of the link 50 about the pin 53 andv relative to the movable abutment 40 results in a slight rocking or tilting of said link relative to the fixed abutment 30 which is readily permitted by the pin 55. It will be observed, however. that two motions or components of motion are imparted to the link 50 as its corresponding movable abutment 40 is adjusted inward or outward, one of these motions or components of motion being that imparted to the link by the lateral or substantially radial movement of the movable abutment 40 and the other being the rocking or tilting of the link.

This arrangement is in contrast with our previous construction in which the link is pivotally mounted on the fixed abutment and has an extensible connection with the movable abutment and has several important advantages. For example, with the present arrangement the direction or path of movement of the link at its sliding or extensible connection more closely approaches a parallel relation to the direction or path of movement of the movable abutment, so hat for any given inward or outward movement of the movable abutment there is considerably less change in the position of the link 50 of the present arrangement relative to the fixed abutment 3!! and relative to the movable abutment 40 than in the arrangement of our previous construction, and this is particularly true with respect to the change in angular relation of the link relative to the track surface on the fixed abutment. The small change in position of the link 50 relative to the abutments, and especially the small change in angular position relative to the track surface on the fixed abutment 30, in

turn provides the related advantage of improved centrifugal force alone may be obtained with the present arrangement at the maximum strokes usually employed with pumps of this character and at strokes considerably greater than those at which such contact between the vanes and vane track surfaces can be maintained by centrifugal force alone with our previous construction. With the present improved arrangement it is thus unnecessary to employ fluid pressure means to urge the vanes outward as they pass through the inletareas and hence it is possible 'to substantially balance hydraulic forces acting on the inner and outer ends of the vanes as they traverse the track surfaces on the links and at the points of transfer between the links and the abutments and vice versa. The improved contour of the vane track surfaces and the balance of hydraulic forcesacting radially on the vanes made possible by the improved contour contribute numerous advantages such, for example, as smoother and less abrupt radial movement of the vanes, decrease in the friction and wear between the vanes and vane track, increase in the output of the pump per revolution of its rotor because of the fluid which is then pumped by the inner ends of the vanes and in-' crease in the pumps efficiency.

It is essential that the vane-contacting surfaces of the links 50 be maintained in vanetransferring relation to the surfaces of the abutments which they connect in order that the vanes may pass smoothly from one of these members to another. It is also necessary that this relation between the track surfaces of the links andabutments be provided at all outputs of the pump, that is to say, at all positions of the movable abutments 40 from their zero or fully inward position to their maximum stroke or fully outward position. The importance of this will be understood from the fact that the rotor is frequently driven at a speed of 1200 R. P. M. or more and that each vane l1 passes to and from each of the track elements during each revolution of the rotor. .It is also essential that the contour of the vane track be such at all outputs of the pump that the vanes are moved outward and kept in contact with the vane-contacting surfaces of the track by the available centrifugal force alone in the preferred arrangement in which the pressures of the fluid at the inner and outer ends of the vanes are substantially balanced during the time that the outer ends thereof are moving outward through the inlet areas. These requirements are met by providing proper contours of the vane-contacting or track surfaces of the trackelements and by arrangement of the pivotal connections between the links 50 and movable abutments 40 and slidable connections between the links 50 and fixed abutments .30 to provide vane-transferring relation between tions of the vane-contacting surface 43 on its on the tongue 52 is kept in vane-transferring re lation with the corresponding portion 36 of the track surface on the arfiis 34 and'the correspondin; movable abutment 40 is adjusted from full strok to zero stroke, 1. e. from its extreme outward position to its extreme inward position. A line so generated has a slight curvature theoretically but this curvature is so small that in practice it often may be neglected and the slots 35 may be substantially straight as in the embodiment illustrated in Figs. 1-11.

reduced end portions 42, is made of arcuate contour concentric with the rotor when said movable abutment 40 is in its half-stroke position, i. e.

when said abutment is midway between its extreme inward and outward positions of adjustment. The portions 36 of the track surface extending from the circumferential ends of the sealing are 32 of each fixed abutment 30 (Figs. 5,

7 and 8) are given a curvature of slightly but gradually increasing radius'so that the vanes I! begin to move radially outward immediately upon leaving the sealing arc 32 and vice versa, but the increase in radius of this portion of the track surface does not exceed the radially outward distance through which the vanes ll can be moved by centrifugal force alone as part of the track surface. In practice each portion 36 of the track surface may be acceptably formed with what for convenience is termed a ,full stroke cam surface, that tour may be made the same as that of the cor-' responding part of a cam for the outer ends of the vanes which would provide constant radial acceleration and deceleration of the varies as they move intermediate the fixed and movable abutments. with the movable abutment in its full stroke position. The track surface on each link 50, however, ispreferably formed with'a half stroke cam surface, that is to say, the track surface on each link 50 preferably approximates a portion of a parabola and is niade such as to provide substantially constant radial acceleration and deceleration of the vanes as they pass there across when the movable abutment 40 is in its half-stroke position. The contour of the character just described extends throughout the length they traverse this is to say, its conof each link except'immediately adjacent the ends of said link as will be more fully explained presently.

The slots 35, which serve as guideways for the pins 55, are so disposed and their configuration made such that all or part of the track surface on the tongue 52 of each link that overlaps the track surface on the corresponding fixed abutment 30, at the extensible connection therebetween, is maintained in vane-transferring rela-v tion with the overlapped part of the track surface portion 36. This vane-transferring relation .is provided throughout all positions to which said link 50 is moved incident to inward and outward adjustment of the corresponding movable abut ment 40 and assures movement of the vanes from one of these track elements to the other which provides smooth, qulet'and satisfactory operation of the pump without materially increased a wear of the vanes or track parts at the Jointed corresponding movable tongue 52 and When straight slots 35 are employed, vanetransferring relation between the overlapping 'track surfaces of the links Ell and fixed abutments 30 at all strokes of the pump may beassured by making the arrangement such that substantially perfect alinement and transfer are provided between the overlapping track surfaces of these parts when the link 50 is in its position corresponding to the maximum stroke position of its movable abutment 40, as illustrated in F18. 7. It is also preferable that the 5) adjacent the tip end of the tongue 52 be slightly straightened," i. e. that the curvature thereof be made less than that of the corresponding portion of the half stroke cam surface," the extreme tip end 58 (Fig, 5) of each, tongue" 52 is rounded off as shown in order to 'aspreferably Y sure that there will be no obstruction to the smooth and uninterrupted movement of the vanes in contact with the track surfaces asthey move across the extensible connection between each link and its adjacent fixed abutment 30. With this arrangement there is a slight intersecting or angular relation between the track surface on the on the arms 34 at the extensible connection between them as the link is moved to positions corresponding to positions of the movable abutment l0 inward from its fullstroke position, that is to say, relation exists theoretically at all strokes except full stroke. This very slight intersecting relation progressively increases, theoretically, as the stroke is decreased'and reaches its maximum at zero stroke of .the pump, as shown in Fig. 8 from which the very slight amount of the angular relation between the track surfaces on the link 50 and fixed abutment30 at fer between them may be observed. The very small amount ofangularity between the track surfaces of the links 50 and fixed abutments 30,

at-the points of vane-transfer oi the extensible connections therebetween, with the arrangement above described does not interfere with vane' transfer and smooth vane action, and satisfactory operation has been obtained at all outputs of a pump employing an arrangement of this general character. v i

Vane transferring relation at the overlapping connections between the-links 50 and movable abutments 40 may be readily provided by so positioning the holes in the' arms 54 of said links and in the abutments reduced end portions 42 that, when the parts are connected by means of the pins 58, the track surface on the forked end i 2 track surface, 51 (Fig.

this slight intersecting the point of vane-transon the forked Q the abutment is in its half-stroke position. Upon movement of a movable abutment 40 outward from its half-stroke position the amount or circumferential length of the portions of the overlapping track surfaces in alinement with one another progressively decreases and vane transfer from one track element to anotifer takes place increasingly nearer the working or pumping arc 4|. Similarly, the point of vjanetransfer moves away from the working arc 4| uponmovement of the abutment 46 inward from its half-stroke position.

As already stated, there is a slight rocking motion or component of motionwf each link 50 about its pin-53 at the movable abutment 60 as said abutment is moved inward or outward to alter the stroke of the pump but this rocking motion is so small that it presents no difficulty in providingv vane-transferring relation at this overlapping connection between each link and its corresponding movable abutment at all outputs of the pump. For example, in a pump having a vane track of the general character described and arranged to provide a} maximum stroke of the vanes of about the pump also having a'rotor of approximately diameter,

face on the'movable abutments may also be relieved in order to assure at all times smooth and uninterrupted movement of the vanes from one the vanes' occasioned by inward protrusion of the track surface on the links 56 since the hydraulic forces acting on the leading and trailing faces of the vanes are substantially balanced during this part of the vanes movement in unison with the rotor.

Fluid is admitted to the spaces between the outer ends of the vanes H as they, approach each .pumping or working arc M and fluid is discharged in like manner as the vanes recede therefrom. This admission and discharge is'accomplished through a pair of diametrically opposite inlet ports 28 and a similar pair of outlet ports 29 formed in each of the, cheek plates 26 and 21, as best shown in Fig. '4 which shows 'an elevation of the rotor face of the casing cheek plate 26. The inlet ports 28 of both cheek plates 26 and 21 are also shown in the sectional view of Fig. 1 and the inlet ports 28 and outlet ports 29 of the casing 'cheek plate 26 are partially shown in Fig. 2. Each of the cheek plates 26 and 21- is also provided, on its face adjacent the rotor I5, withv two pairs of arcuate vane slot ports 60 and 6|, respectively, which are positioned to register successively with the inner-ends ofthe vane slots as the rotor revolves. The vane slot ports 60 are connected with the inlet ports 28 by radial grooves or passages 62 on the outer faces of the cheek plates 26 and 21 and similarly the vane slot ports 6| are connected with the outlet ports 29 by the passages or grooves 63, as will be understood from Fig. 4. The vane slot ports 66 and radial grooves 62 of both cheek plates 26 and 21 are also shown in the sectional view of Fig. 1. The. arrangement is such that the inner ends of the vane slots are connected with fluid under the same pressure as the fluid acting upon the outer ends of their of these track elements to-another and in order to compensate for any small errors in manufacture. It'is also preferable that the links 50 have little or no vane contacting surface which extends beyond the centers of the pins 53 toward the pumping arcs 4|. It is further usually preferable that the links 50 be arranged to extend as close as possible toward the pumping arcs it, thus making it possible to keep to a.

minimum the vertical dimension of the movable abutments 40 which is frequently desirable.

Due in part to the fact that the links 50 are rigid and are .provided with track surfaces of non-uniform (i. e. non-circular) curvature, the vane track hereinbefore described does not assume true circular outline when the movable abutments 40 are moved inward to their zero stroke position, at which the pumping arcs 4| are spaced from theperiphery of the rotor I5 .by

a clearance equal to the clearance at the sealing arcs 32. With the track elements adjusted to their zero stroke position, therefore, the diameter of the vane track at the sealing arcs 32 is not its smallest diameter, as may be'observed in-Fig. 8 in which the portion of the link just beyond the tongue 52 is separated. from the peripheral surface of the rotor by a clearance less than that between said rotor and'the sealing arc 32. The diameter of the rotor i5 is thus determined by the vane trackat this region of the links 50 when the parts are in zero stroke position, and the clearance between the rotor i5 and sealing arcs 32 must be correspondingly greater than would otherwise be required. The operation of the pump is not adversely affected by this increased,

clearance or by the slight radial movement of slanted passages 66.

minimum diameter of the corresponding vanes l1 while said vanes are movingintermediate the fixed abutments 30 and movable abutments 40, and vice versa, and hence is supplied to the inner ends of such vanes to assist in'holding their ends firmly in contact with these portions of the vane track surface as they move thereacr'oss.

The fluid circuit further includes a branched inlet conduit 64 and a branched outlet conduit 66' formed in the casing III as shown in Figs. 1 and 3. The inlet conduit 66 is connectedby slanted passages 66 with inlet ports 28 of the casing cheek plate 26 (Figs. 1 and 3) and the outlet conduit 65 is connected with the two outlet ports 29 of said casing cheek plate 26 as by slanted passages 61 (Fig. 3) similar to the Fluid is supplied to the pump, as from a suitable reservoir, not shown, through an inlet pipe 66 and fluid is discharged by the pump into the outlet pipe 69 which may be connected with any suitable hydraulic device that is to be operated thereby.

When the rotor I5 is driven in a counter-clockwise direction as viewed in Fig. 2 fluid enters through the inlet ports. 26 of the casing cheek plate 26 and passes into the connected inlet areas of the two pumping sections of the pump. Pumping is accomplished by the vanes H as they move across the working or pumping arcs 4i and the vanes I! thus force fluid into the outlet areas of the two pumping sections from which it passes out through the outlet ports 28 of the casing cheek plate 26 and into the outlet conduit 66. As already explained, the size of the pumping'chambers and the volume'of fluid delivered by the pump per revolution of the rotor l are determined by the distance of the pumping arcs 4| from the periphery of the rotor l5; as this distance may be varied by'inflnitely small increments from minimum to maximum, the size of the pumping chambers and, hence the volume of fluid delivered by the pump may be likewise varied from minimum to maximum or vice versa by adjustment of the movable abutments 46. The novel and improved means provided for ad justing the abutments to alter the delivery or stroke of the pump will now be described.

Referring to Fig. 2, fluid under te same pres sure as that in the'outlet ports 28 acts upon the connected portion of the radially inner end of each movable abutment 46 and-exerts thereon a force tending tomove said abutments radially outward as far as permitted by other parts of the adjusting and control means. Each abutment 46 is also urged radially outward by a double torsion type spring 16 (preferably made of spring wire of rectangular cross section, as

. shown) which is capable of movingsaid abutment radially outward when little or no'pressure' exists in the discharge ports 29 of the pump. Each of the two springs 161s positioned in a portion of the recess 24 (Figs. 1 and 2) formed in the outer circumference of the spacerring 26. The width or axial dimension of the recess 24 is less than that of the web portion 2| of the spacer ring 26, as shown in1Fig. l, andwas shown in Fig. 2 said recess 24 has a non-uniform radial depth relative, to the outer circumference of the spacer ring 26 in order to provide the space necessary to accommodate the several elements of the adjusting and control means which are ends by pins 82 and 88 respectively which are carried by the side walls of the flange portion 23 of the spacer ring, the arrangement being such that all parts of said bell cranks are disposed within the outer diameter of the spacer ring 26 at all positions to which said bell cranks are moved incident toadjustment of the corresponding movable abutment. 46 from its full stroke position to its minimum or zero stroke position. The partial sectional view of Fig. 2 shows the bell cranks 86 and 8| for only one of the movable abutments 46 but it will be understood that a similar pair of bell cranks (the pivotal mountings 82 and 83 for which are shown) are provided for the other movable abutment 46, the arrangef ment for both abutments being identical.

As best shown in Fig. 10, the end of the arm 84 of the bell crank 86 is forked as at 85 to receive the reduced outer portion 46 of its movable abutment 46, one leg of the forked end 85 extending on either side of said reduced outer portion 46 as will be understood from Fig. 2. The forked end 85 of the bell crank 86 is operatively connected with the corresponding movable abutment 48 by means of a pin 8'! (Figs. Sand 11) which is mounted in a hOle drilled horizontally through the reduced outer portion 46 of the abutment, as will be understood from Fig. 6 which shows the pin a-l in place in said hole. The pin 81 is provided with flattened end portions 88 (Figs. 2, 6 and ll) which slidingly flt in slots 86 formed in the forked end 85 of the bell crank 86. With this arrangement the bell crank 86 is free to move angularly with repositioned. in .said recess at different points around said recess circumference.

Each of the two double torsion type springs 16 includes a central double arm portion H (Fig. 9)

with a hair-pin end 12 which enters and slidingly engages, a notch or slot 41 (Figs. 2 and 6) in a reduced outer portion 46 of the corresponding movable abutment 46, said reduced outer portion 46 having a substantially rectangular cross-section as best shown inthe perspective view of Fig. 6. The coiled portions I8 of each spring I6 are mounted upon a center piece 14 (Figs. 1 and 2) which in turn is supported by a pin I5 carried by the side walls of the flange portion 29 of the spacer ring 26. Each spring 76 also includes a pair of arms I6 (Figs. 2 and 9) extending from the coiled portions 18 and having hooked ends H which engage a pin I8 that is also carried by the side walls of the flange portion 28 of the spacer ring 26. With this arrangement each spring 16 is supported by the spacer ring 26 andall parts thereof are disposed within the outer diameter of said spacer ring 26.

- Each movable abutment 46 is moved inward by means of a pair of co-operating levers or bell cranks 86 and 8| respectively which also limit and controlthe maximum outward position to which said abutment 46 is permitted to be moved spect to its abutment 46 as said bell crank swings on its pivot 82, the pin turning in its hole to provide sliding area contact between the flattened end 88 and the side walls of the slots 86. It will also be observed that the shoulders 89 (Fig. 11) formed by the juncture of the flattened end parts 88 and the central round portionof the pin 81, in cooperation with the .side faces of the forked end 85, prevent displacement of the pin and keep it in proper operating position at all times.

The end 8| of the arm 86 (Figs. 2 and 10) of the bell crank 86 is reduced in width to receive the correspondingly forked end 83 of the arm 84 of .the bell crank 8|. The reduced end 8| is provided with a hole to receive its pin 81, identical with the pin 81 already described, the flattened ends 88 of which are-slidingly fitted into the slots 86' in the forked end 88 of thearm 84. and the two bell cranks 86- and.8| are thus operatively connected with each other for simultaneous movement.

The arm as of the bell crank s is adapted to be moved inward by any suitable means, and the arrangement is preferably such that the bellcranks 8| for both movable abutments 46 are moved inward by a common member so that the abutments 46 are equally and simultaneously moved. As here shown, the arm 98 is provided by its spring 16 and the internal fluid pressure in the pump. The bell cranks' 86 and 8| are; positioned in the recess 24 of the spacer ring 26 i and are pivotally supported intermediate their .75

adjacent its end with a raised portion 81 of partially arcuate contour whichis adapted to slidingly bear-against the inner end of a reduced rod 88 (Fig.- 2) extending inward i'rom an adjusting piston 88 reciprocable in an adjusting cylinder l6l, said piston being provided with a suitable packing I66 to prevent leakage of fluid from the adjusting cylinder. With this arrangement inward movement of the adjusting piston 88 causes the bell cranks 86 and 8| to swing about their, pivotal mountings and move both movable abutments 46 inward to reduce the stroke and output of the pump. Outward movement of the adjusting piston 99 permits the'bell cranks, to swing about their pivotal mountings in the opposite directions (1. e. opposite to the directions of their swinging when the adjusting piston 99 moves inward) and the movable abutments 40 are moved outward by the internal pressure of the fluid in the pump and the spring I as far and as rapidly as permitted by outward movement of the adjusting piston 99.

The position and/movement of the adjusting piston 99 thus controls the position and movement of the bell cranks 90 and 9| and of both movable abutments l0. Inward movement of the adjusting piston 99 is effected by admitting presof pressure fluid on the outer end thereof and, because both movable abutments 40 are moved inward and their outward position controlledby said adjusting piston, the limit screw also serves-- to limit the minimum stroke of both of said abutments 40. The load imposed on the limit screw I is not excessive when it engages the bell cranks arm 90 to thus limit the minimum stroke of the two abutments 40, this load being only the sure fluid to adjusting cylinder IOI through the passage I02 and its connected conduit I03, such pressure fluid being supplied by any suitable source, not shown. Outward movement of the trol means, not shown, which form no part of the present invention and a number of which are well known in the art.

This novel and improved adjusting and control means has many advantages. For example, it is entirely housed within the enclosing casing of the pump, as already mentioned. It provides sidifference between the inward force exerted on the adjusting piston 99 by action of pressure fluid on the outer end thereof and the combined forces exerted on both abutments 40 by action of internal pump pressure on their inner ends and by the springs I0.

Another important feature of the present invention is that the pump is easy to assemble and its parts are readily accessible for inspection and replacement. In assembly, the shaft I9 is first put into place. All of the vane track elements,

the springs 10, bell cranks 80 and 9| and the casing cheek plate 29 are then assembled on the spacer ring 20 while said spacer ring is out of the casing I0; the spacer ring-20 and parts. carried thereby may then be put into place in the casing I0 as an assembled group or unit. The rotor I9 and vanes I! are next put into place, followed by the end head cheek plate 21 and the cavity in the casing I0 is closed-"by fastening the end head multaneous and equal movement of the two movable abutments 40, thus accurately regulating the output of the pump and assuring equal strokes of the vanes at both of the abutments to thereby provide' substantially equal and opposite torques at opposite sides of-the rotor which form a couple. substantially straight line" relationship between movement of the adjusting piston 99 and the movable abutments 90; upon any movement of the adjusting piston 99 and abutments 90, one hell crank 90 or 9| of each pair will swing about its pivot in a clockwise direction and the other will swing in a counter-clockwise direction, so

that variation from the straight line" relation that might be due to angular movement of one bell crank is substantially compensated and balanced by'the opposite angular movement of the other bell crank.

Simple and novel means are also provided for limiting as desired the minimum stroke position to which the movable abutments 40 may be moved by the adjusting piston'99. Referring to Fig. 2,

the casing I0'is provided with a limit screw I05 having a lock nut I06 and a sealing cap I01. The inner end of the limit screw I05 is adapted to engage the reduced en'd M of the arm 90 of the bell crank 90 when said bell crank has moved to its position corresponding to the desired maximum inward position and minimum stroke of the movable abutment 90, which minimum stroke may be altered at will by merely adjusting the limit screw I09 and without disturbing any other part of the pump. Since the limit screw I05 limits the outward swinging movement of thebell crank arm. 90, it also acts to limit the maximum inward position to which the adjusting piston 99 can be moved by action It also makes it possible to provide II to the casing I0. QThe adjusting piston 99 is next inserted and the adjusting cylinder II" is closed by it's cover l0 All of the vane track elements, the rotor l5, nd vanes I1 may be inspected by merely remoying the end head II and end head'cheek plate 2-]. If desired, the spacerring 20 and all parts caisried thereby may be removed for inspection or placement without disturbing the connections between the pump and the, inletv pipe 99, outlet pipe 99 or conduit I09, it being merely necessary to remove the end head II, end headcheek plate 21, rotor I0. vanes l1 and adjusting piston 99. All working parts are thus quickly and conveniently accessible.

In the embodiment hereinbefore described each link member 50 of the vane track assembly has an extensible connection with the adjacent fixed abutment, 30 and also has a pivotal mountinl near its end adjacent the corresponding movable abutment 40, this pivotal mounting being carried by the movable abutment 40 and hence having a fixed positional relation thereto. This arrangement is preferred because of its simplicity and it is now thought that it will answer requirements in a majority of instances, but numerous modifications may be made. For example, the pivotal mounting of the link may be arranged to have a changing positional relation with both the fixed and movable abutments. An arrangement of this character is illustrated in Figs. 12, 13 and 14 in which the modified vane track .elements are illustrated in connection with a modified annular spacer ring I20, the latter being shown in section with parts thereof broken away for convenience in illustration.

The modified vane tra'ck elements shown in Figs. 12-14 include a pair of modified movable abutments I40 mounted opposite one another in parallel slideways formed in the modified spacer ring I20 and a pair or modified fixed abutments I30 (one of which is shown in Figs. 12 and l3) which are'likewise mounted in suitable recesses at the vertical center line of the spacer ring I20 and are held in place by screws 9 I The modified vane track elements also include four substantially rigid interconnecting track members or movable abutments 40 fora which extend between and connect the track surfaces of the abutments in themanner illustrated in Fig. 12, the arrangement being generally the samein this respect as that of the embodiment previously described. The interior or vane contacting surfaces of the movable. abutments I40, fixed abutments I30'and links I50 may have the same contours as those described in connection with the embodiment of Figs. 1-11, but theportion of the track surface 51 near the end oi'the link adjacent the fixed abutment may frequently be provided with a greater curvature than in the embodiment of Figs. 1--11 above mentioned.

The movable abutments I40- are in most re- 1 2,813,246 links I54 (two of which are shown in Fig. .12)

respectively. The cam surfaces I51 and I50 are arranged to contact the pins I45 and I35 respecments I40 and fixed abutments I30, as shown in tivelywhich are carried by the movable abut- Flg. 18, and the cam surfaces I 51 and I58 are made of such contours that when they are in contact with the pins- I45 and I35 respectively spects the same as the movable .abutments 40 pre -viously escribed and the parts of. said abutments I40 similar to corresponding parts of said abutments 40 will be referred to by the same reference numerals used in connection with the latter. It will be noted, however, that the'vertical dimension of each of the modifiedmo' ble abutthe portions of the track surface on the ends of the link I50 are disposed in vane-transferring relation'with the overlapping track surfaces on thecorresponding movable and fixed abutments at all positions of relative movement of the track elements incident to adjustment of the correspending movable abutment I40 between its exments I40 is greater than that of'the abutments.

40,- this difference in vertical dimension providin reduced end portions I42 of'the modifiedfmovable abutments I40 whose vertical dimensionsex-,

ceed those of the reduced end portions 42fcfthe pur e thatiwill; be explained subsequently.

The fixed abutments I are providedwith reduced end portions I34 which extend from the central portion I32 (Fig. 13) and whichare conveniently provided with a full stroke cam surface" 36. It will be observed that .theredirced end portions I34 extend from the sealing arc 32 in generally horizontal and circumferential directions for a distance greater than that of the treme inward and outward positions.

The cam surfaces I51 and I58 on each link I50 are kept in contact with their corresponding pins I45 and I35 by means of a tension spring I65 (Fig. '12) one end of which is attached to the rocking lever I60 as by a hole I64 (Fig. 13') and the other end of which is attached to a pin I66 arms 34 of the fixed abutments 30 and each re- I duced end portion I34 is provided with a hole to receive a pin I35,- these pins I35 being shown in place on said reduced end portions I34 in Fig. 13.

Each link I50 is formed at both its ends'with forks I5I and I52 (Fig.- 13) respectively which" are arranged toreceive the reduced end portions I42 and I34 respectively of the movable abutments I40 and fixed abutments I30, the track surface on the forked ends of the link I50 overlapping the traclg surface on said reduced end portions I42 and I34 in all positions of adjustment of the track elements. Each link I50 is provided with a pivotal mounting which is preferably positioned near'the end of said link adjacent the corresponding movable abutment I40. In this embodiment-this pivotal mounting is provided by a short forked arm I54 extending from 'the outer'surface of the link I50 and having a hole for a pin I53 which also extends through the adjacent end of a member I60 which for convenience is termed the rocking lever." Each rockinglever I60 extends into its corresponding recess I25 formed in the modified spacer-ring I20 and is pivotally mounted on the side walls of said abutments by means of a cam or guide surface formed on one of the elements and by a member or surface carried by the other of the elements and'which is adapted to contact said guide or cam surface; that is to'say the cam or guide surface may be carried by the abutment and o the contact member or-surface may be carried recess by a pin IBI which extends through saidv (Fig. 12) carried by the side walls ofv the recess I25.

with this arrangement the spring I pulls the rocking lever 'I (Was far and as rapidly toward the corresponding'movable abutment I40 as permitted by the cam surfacev I5'I'wi'1ich engages the pin I45, the link I50 swinging about the pin I 53 at its pivotal mountingjon the inner end of the rocking lever I60 so that the cam surface I 50 is kept in contact with the pin I35 on. the fixed abutment I30 and thus assists in limiting the movement of the'rocking lever l60 and in determining the relative position of said rocking lever I60 and said link I50 conformably with the position of the corresponding movable abutment I40. Upon outward movement of the movable abutment I40 the spring I65 immediately swings the rocking lever I60 outward or toward said movable abutment and keeps the cam surfaces I51 and I58 in contact with the pins I45 and I35 respectively, the parts occupying substantially the positions shown in the left hand half of Fig. 12 when the movable abutment I40 is adjusted to" its full stroke position in which it is there shown. Upon inward movement of the movable abutment I40, the pin I45 acting against the cam surface I51 exerts force upon the link I50 which is slidingly resisted by the contact between the cam surface I 58 and'pin'l35, so

that the rocking lever I60 swings inward against the-tension of the spring I65; the parts occupy substantially the positions shown in the right hand half of Fig. 12 when the corresponding movable abutment I40 is adjusted to its extreme and direction of inward or outward adjustment of the movable abutment I40. Each link I50 is thus positioned by its swinging pivot I 53 and the contact between the cam surfaces I51 and I58 and the pins I45 and I35 respectively.

The arcuate movement of the pivot I53 for I51 and I58 respectively (Fig;

spending movable abutment.

i alone at all strokes each link I00, the cam surfaces I01 and I and pins I40 and I30 cooperate to produce movement of the link I00 in its entirety in a general circumferential direction relative to both its corresponding movable abutment I40 and fixed abutment I30 or relative to the rotor. This will be understood from comparison of the positions of the parts shown in the left and right'h'and sides respectively of Fig. 12 in which it will be observed that the end of the link I00 is nearer the pumping are H of its movable abutment I40 when said abutment is in its full stroke position shown at the left hand side of Fig. 12 than when the movable abutment is in its extreme inward or zero stroke position shown at the right hand side thereof. This circumferential movement may also be seen in the diagrammatic view of Fig. 14 in which the fulllines show the position of the link I00 relative to its corresponding fixed and movable abutments when said movable abutment is in its zero stroke position and in which the dotted lines show the position of the link relative to these parts when its movable abutment is in its extreme outward or full stroke position. This arrangement. therefore, provides an extensible connection not only between the fixed abutment I30 and adjacent end of the link I00 but also between the movable abutment I40 and'adiacent end of said link I00. It is in order to accommodate the relative movement between the link I00 and movable abutment I40, due to this generally circumferential movement of the link and change in relative position of these elements at the extensible connection between. them, that the vertical dimension of the modified movable abut-' ment I40 is made greater than the vertical dimension of the abutment 40 of Figs. 1-11 thus providing greater length of the reduced end portion I42 of the modified abutment I40 and of the portion 43 of the track surface thereon. The movement of the end I02 ofthe link I00 relative to the adjacent fixed abutment I30 at the extensible connection therebetween extends through a greater distance in the general direction of the track surface on said fixed abutment movement and positionsof the corresponding movable abutments I40, the links I00 being moved conformably with the extent and direction of movement of the movable abutments I40, and this is accomplished without attachment of the links to either the fixed or movable abutments.

The arrangement of Figs. 12-14 further pro-- vides especially smooth vane-transferring relation and'good alinement of the track surfaces of the ends of the links I00 with respect to the overlapping track surfaces on the fixed and'movableabutments at the extensible connections therebetween, with little or no angular or intersecting relation between the track surfaces on said links and on said abutments at the points of vane transfer. rhis is particularly true at the more critical. regions adjacent fixed abutments I where the radial velocity of the vanes is relatively low, as mentioned earlier. This improved relation' betwee .the track surfaces of the links and the abut ts at their extensible connections is in part due to the greater circumferential move ment of the links relative to the abutments and .in part to the fact that the links are progressively I00 than in the case of the extensible connection between the link 00 and fixed abutment -30 of the embodiment of Figs. l-ll, and it is for this reason that the reduced end portions I34 of the modified fixed abutments I30 extend for a great-- er distance than the arms 34 of the fixed abutments 30. The generally circumferential movement of each link I00 relative to its fixed abutment I30 is also greater than the horizontal or radial distance moved by the corresponding movable abutment I40 upon adjustment thereof to alter the stroke and output of the pump and the length of the trackway; and greater than the change in circumferential length of the portion of the vane track intermediate the pumping are H and sealing are 32 on the movable and fixed abutments which said link connects. It will also be observed that the track length increases at the extensible connection between the link and one of the abutments and simultaneously de-" creases at the extensibl connection between the opposite end of the link and the other abutment upon inward or outward adjustment of the corre- The arrangement of Figs. 12-14 provides contour to the vane track whichthe vanes I1 can follow under the influence of centrifugal force usually employed with pumps of this character. It also provides movement and positions of the links I00 coordinated with the rocked outward or toward more nearly horizontal positions as they are moved toward their positions corresponding to minimum or zero stroke position of the movable abutments I40. This outward rocking of the links I00 will be best understood by reference-to the diagrammatic view of Fig. 14 in which the line A-B has been I drawn tangent to the track surface at a point on the link I00 near its end adjacent the fixed abutment I30 when the link I00 is in its position corresponding to full stroke positionof its movable abutment I40 and in which the line A'B' isdrawn tangent to the same point on the track surface of said link'I00 when said link is in its position corresponding to zero stroke position of its movable abutment I40. The angle, designated by the letter C, between the lines A-B and A'B' indicates the extent of rocking of the line I00 outward or in a direction generally toward a line tangent to the sealing arcs 02 upon adjustment of the corresponding movable abutment from its extreme outward position to its extreme inward position, this rocking of the link I00 taking place progressively as said movable abutment is moved inward. With this arrangement the track surface on the end I02 of the link I00 is .abutment I40. .Two motions or components of motion are thus imparted to the link I00 upon inward or outward adjustment of its corresponding movable abutment I40, these motions or com-' ponents of motion comprising respectively. the rocking or tilting of thelink and its movement in a general circumferential direction above described. The periphery of the rotor is indicated by the dotted circle H0 in Figs. 12 and 14.

A convenient method for determining the location of the pivot IOI for the outer end of the rocking lever I00, the length of said rocking lever I00 and contour of the cam surfaces I01 and I00 may also be best understood by reference to Fig.

14. According to. this method the movable abutment I40 is first adjusted to its full stroke position, as indicated by the dotted'line F3 in Fig. 14. and the link I00 is likewise placed in its correward.-

pivotal connection I53 and the pivot point II in 2,818,246 spending full stroke position and is disposed so that the track surfaces on its ends are in smooth vane-transferring relation with the overlapping track surfaces on the movable abutment I40 and fixed abutment I30; for convenience and clarity in illustration the outline of the link I50 in its full stroke position has been partiallyshown in dotted lines in Fig. 14 and the outline of the fixed abutment I30 has also been partially so shown in this figure. The point of pivotal connection I53 of the link- I50 to the rocking lever I60 is then selected and is preferably located as close to the end of said link- I50 adjacent the movable abutment I40 as permitted by constructional requirements and withoutinterference with the corresponding movable abutment I40, as indicatedby fixed abutments m respectively, preferably at' points approximately as shown in Figs. 12 and 13;

the pins I05 and I45 have not been shown in Fig. 14 to avoid confusion. The contours of the cams I51 and I50 are then determined by adjusting the movable abutment I40 from its extreme inward position to its extreme outward position while swinging the link I50 and the rock-.

ing lever I50 and with the track surfaces on the ends of's'aid link I50 maintained in smooth vane-transferring relation with the overlapping track surface on the abutments at all positions of adjustment of said movable abutment I40 and at all corresponding positions of said link I50.

the letter D in Fig. 14; this preferred location of' the pivotal connection In-makes possible the use of a rocking lever I60 of minimum length or provides best results with a-rocking lever I60 whose length exceeds such minimum. The movable abutment I40 and-link I50 are then moved to their .minimum or zero stroke positions, with the link disposed so that the track surfaces on its ends are in smooth vane-transferring relation with the overlapping track surfaces-on the fixed and movable abutments at the points of vane, transfer therebetween; the outline of the track surface of the movable abutment I40, in its minimumor zero stroke position is indicated by the dotted line MS in- Fig. 14 and the outline of the link I50 in its corresponding position is partially shown in full lines. With the link I50 in itsminimum stroke'position, the pivotal connection I53 will then have moved to the point E in Fig. 14.. A line between the points D and E, if drawn, would'then represent the chord of the arc of swing of the pivotal connection I53 from its full stroke position to its zero stroke'position and a line F-G is next drawn perpendicular to and bisecting said imaginary chord DE; the chord D-E has not been drawn in Fig. 14 in order to avoid confusion with other lines of that figure and it is not necessary that said chord be drawn for purposes of construction or design. The pivot I6I for theouter end off'the outer end of the rocking lever I60 isthen preferably located either at the intersection of the lines F+G and E-H, as in this embodiment, or at a point on the line FG radially outward from said intersection. This preferred location of the pivot point I5I has several advantages among which is that the .portion of the track surface on the link I50 adjacent the pivotal connection I53 occupies its position of closest proximity to the rotor when said link is in its position corresponding to the minimum or zero stroke position-of its movable abutment I40; this preferred location also assures satisfactory co-operating action of the cams I51 and I58 and pins I and I35 respectively as said movable abutment I40 is adjusted inward or out- The above described location of the turn. establish and determine the rocking lever I50.

The ccntours of'the camsurfaces I51 and I58 are next determined. This is accomplished by first more or less arbitrarily positioning the pins I45 and I05 on the movable abutment I40 and length of the The contour of the cams I51 and 158 may thus be said to be along lines generated by contact of the outer surface of the link with the pins I45 and I35 respectively as said .link is moved in unison and con'formably with'its movable abut- -ment- I40 while continuously maintaining the overlapping track surfaces on the ends of the link. and on. thejabutments in smooth vane-transferring relation with one another.

The method above described provides excellent vane-transferring relation and'alinement between the track surfaces of the track elements at the overlapping extensible connections between them. ,At positions of the track'elementscorresponding to the full stroke and zero or minimum stroke positions of the movable abutments I40 the vanetransferring relation and alinement of the track surfaces at the points of vane transfer are practic'ally perfect and, although the arcuate move-- rnent of th swinging pivotjl53 theoretically resuits in less perfect alinement at intermediate strokes, the resulting departures are so slight B that they are almost undiscernible by inspection and the relation of the track elements to one another atall strokes is such as to provide particularly smoothyane action and highly satisfactory operation of the pump. Whenthe modified track'elements of Figs. 12-

14 are employed with the improved adjusting and control means shown in Figs. 1, 2, 10 and 11, it

is necessary to increase theouter diameter of the spacer ring, and hence the diameter of the casing, in order to provide a spacer ring such that the inner recesses I25 thereof for th rock ing lever I60 would not extend into and connect with the outer circumferential recess 24 for the parts of the improved adjusting and control means of Figs. 1, 2 10and 11.

of illustration, therefore, the modified spacer ring For convenience I20 and modified track elements of Figs. 12-14 are shown as adapted for use with conventional adjusting and control means of any preferred type. As shown in Fig. 12 each modified mov-.

' able abutment I40is provided with an adjusting rod I80 which is operatively connected with its abutment as by a threaded connection I8I shownin dotted lines and whichextends through an appropriate opening in themodified sp'acer ring I20 and in the modified enclosing casing '(not shown). The end of each adjusting rod I8I is flattened. as at I82 to receive the forked end of a link I84 and the two parts-are connected as by a pin I83. The links 184 may be attached to any appropriate conventional adusting and control means, several of which are-known in the art.

" responding elements shown in Figs. 12-14, differ- I Figs. 16 and 17 illustrate modified vane track elements and a modified spacer ring which are generally similar in many respects to the corwith the movable abutments I40 of Figs. 12-14 and the modified fixed abutments 230 of Figs.

15-17 differ from the fixed abutments I30 only in'that the pins I35 of said fixed abutments I30 are omitted as they are not required in this modification. The modified spacer ring 220 of Figs.

.15-17 is also the same as the spacer ring I20 of Figs. l2-14 except for the size and shape of the internal recesses225 for th inner ends of the rocking levers.

' The modified links 250 of Figs. 15-17 are'the example at a point radially outwardfrom the intersection of the lines F-G and EH,. would require corresponding outward movement or same as the links I50 of Figs. 12-14 except that the cam surfaces I50 on the end of the link adjacent the fixed abutments are omitted in the modified links 250 and also in that the outer surface of ,each modified link 250 is provided not only with a short forked arm I54 but also with another short forked arm 254 which i preferably disposed as near as practical tosaid arm I54.

Each'modified link 250 is pivotally supported upon its short arms I54 and 254 by means of pins I53 and 253 respectively carried by the inner ends of a pair of rocking levers I00 and .260 respectively. The rocking lever I00 of Figs.

15-17 and its associated parts may be the same as described in connection with Figs. 12-14 and are approximately so shown, hence require no further description; The inner end of the rocking lever 260 ispivotally connected to the short arm 254 extending from the outer surface of the link 250 by means of a pin 253 as above stated and the outer end of said rocking lever 280 is, pivotallysupported by a pin l extending therethrough and into the side walls of the spacer recess 225 of the spacer ring 220.

In designing vane track elements ofthe character shown in.Figs. 15-17, the location of the pivot .point 253 may be arbitrarily chosen within certain limits but it is preferable to position it as close as practical to the pivot point I 53. which is preferably first located as hereinbefore explained, in order that the length of the rocking lever 260 may be kept to the minimum and also to assure that the short arm 254 will not strike the fixed abutment 230jwhen the link 250-is in its position corresponding to the mini-mum or zero stroke position of its movable abutment I40. A slight change in the location of the pivot point 253 will make a considerable difference in the cation of the pivot point 20I for best-results. The location of the pivot points iii and 26I in conformity with one another is. preferred although acceptable but perhaps less perfect results may be obtained with other arrangements.

The functioning of the arrangement of Figs. 15-17 is generally the same. as that explained in connection with the embodiment of Figs. 12-14. Each link 250 is moved conrformably with the extent and direction of the inward or outward movement of its corresponding movable abutment I40 and the approximate relative positions of the parts when the corresponding movable abutment is at its full stroke position may -be observed in the left hand side of Fig. 15 and. the positions of the 'parts when the corresponding movable abutment is in its minimum or zero stroke position may be observed in the right hand half of that figure. Each link 250 has an extensible connection both withits fixed abutment 230 and movable abutment I40 and said link moves inla generally circumferential direction relative to both of said abutments, with itsmovement rela' tive to the fixed abutment exceeding both the radial distance moved by themovable abutment I40 and the corresponding change in theclrcumferentia1 length of the vane track intermediate .the embodiment of Figs; 1244 so that two motions or components of motion are thus imparted to the link 250. The path of movement of each link 250 isdetermined, however, by its pivotal mountings and its rockin levers I60 and 260, and the extent of its movement in this path is determined by the cam surface I51 and the pin I length of the rocking lever 260, as may be judged by the relative lengths of the rocking levers I and 260. The location of the pivot point 26I and the length of the rocking lever 280 are determined in the same manner as already described in connection with the rocking lever I60 of Figs. 12-14 and will be understood from that descriptionand from the construction lines therefore shown in- Fig. 17 without further explanation. It

is desirable, however,. that the location of the pivot point 26I for the outerend of the rocking lever 260 shall be in conformity with the locationof the pivot point IGI for the outer end of the rocking lever I00 in order to assure proper movement of the link 250 and proper relation of the track surfaces thereon that overlap the track surfaces on the fixed and movable abutments at the extensible connections between lines F-G and E'-H and the pivot point 26I is similarly located at the intersection of the corresponding lines FF-GG and EE-HH; selection J of another location for the pivot point ISI, for

on its movable abutment I40. The path and extent of movement of the link 250 thus co-operate to determine itsposition so that no cam surface is required for positioning the track surface on the end of the link adjacent the fixed abutment with respect to the overlapping track surface on said fixed abutment, smooth vane-transferring relation at the extensible connection being provided by action ofthe rocking levers and pivotal mountings.

The modified vane track elements illustrated in Figs. 18 to 22 inclusive provide between the interconnectinjg'track members or links and the in the cheek plates as will be presently explained.

The modified vane track elements of Figs. 18-22 include apair of oppositely positioned modified movable abutments 340, a pair. of oppositely positioned modified fixed-abutments 330 (one .of

which is shown in Fig. 18) and four interconnecting track members or links 350 (two of which are shown in Fig. 18). The general arrangement of these parts relative to each other is similar to that of the embodiments previously described and will be understood from Figs. 18 and 19.

The modified fixed abutments 330 are here shown as identical with the fixed abutments 30 of Figs. 1-11 except that the arms 334 of the abutments 33!) extend from the sealing arcs 32 in horizontal and-generally circumferential directions for distances greater than in the case of the arms 34 of said fixed abutments 30. The greater horizontal and generally circumferential lengths of the arms 354 is to accommodate the movement of the adjacent ends of the link 350 with respect to the fixed abutments 330, the relative movement between these parts at their extensi-ble connections exceeding the corresponding relative movements between the links 50 and fixed abutments 30 ofthe embodiment of Figs. 1-11 in the same manner and to substantially the same extent as explained in connection with the modification of Figs. 12-14.

The modified links 353 are also similar to the. links 50 of the embodiment ofFigs. l-11 from which each of them differs p ncipally in that the slot at ,the forked end Jl extends into the link 35!! for a distance greater than that of the slot at the forked end'5l of said link 50, in order to provide for the c .tensible connection between the link 350 and its movableabutment 343, and also the length of the tongue 352 of the link 350 exceeds that of the tongue 52 as they lengths of the modified inlet ports 32 3 and their port extensions 328--are substantially the same as the circumferential lengths of the inlet ports 28 of the cheekplat'e 25 (Fig. 4) and hence said inlet ports 323 and their port extensions/323 supplyfiuid to the. outer; ends or the vanes I] approach the pumping arcs 4i. Similarly, the combined circumferential lengths of the modified outlet ports 329 and their port exof the link 50in order to accommodate the greatg er movement of the link 350 relative to its fixed abutment 330 at the extensible connection therebetween. It will be observed that the pin 353 which is carried by the arms 354 at the forked end i of each link 350 extends beyond the side edges of said link for a purpose which will presently appear.

The movable abutments- 340 are shown as similar to the abutments I of Figs. 12-14 from which they differ principally in that each abutment 340 is provided on each of its reduced end portions 342 with a cam or guide slot 355 for the pin 353 to be more fully described subsequently.

The modified vane track elements of Figs.

- l8-22 have been shown in connection with a fragmentary side or -end elevation of a modified spacer ring 320 (Fig' 18) which is generally similar to the spacer ring I20 of Figs. 12-14 except that no inner recesses are required The vane track elements of this embodiment may also be employed, however, with aspacer ring 23 shown 7 in Figs. 1 and 2 together, with the improved adjusting and control means of Figs 1, 2,' 10 and 11 without appreciable increase in the outer .diameter of said spacer ring 20 or of the enclosing casing.

Modified cheek plates are also employed with this embodiment of the vane track elements, the arrangement of which will be understood from Fig. 20 which shows an elevation of the inner or rotor face of a modified casing cheek plate 325. which is identical with the casing cheek plate 26 of Fig. 4 except in particulars now to be explained; the modified casing cheek-plate 326 is also partially shown in Fig. l8.- Referring to Fig. 20, the modified casing cheek plate 325 is provided with a pair of modified inlet ports 328 and a pair of modified outlet ports 323 which are provided at the ends thereof adjacent the horizontal center line with shallow recesses or port extenmodified cheek plates are also each provided with four cam or guide slots 325, one of which 'is disposed adjacent the closed endof each of the port extensions328' and-329' as will be understood from Fig. 20. The guide slots 325 are adapted to engage the ends. of the pins 353 and hence are made deeper (relative to the rotor face of the cheek plates) than the port extensions, as will be best understood from the fragmentary view of Fig. 22. It will also be understood that the end head cheek plate 321 for use with the vane track elements ofthis embodiment is similarly and correspondingly modified to provide port extensions and-guide slots mating with those of thecasing cheek plate 326 as will also be'understood from the fragmentary view of said cheek plates 326 and 321 in Fig. 22.

With this arrangementeach link 350 is moved in a generally circumferential direction relative to both its fixed abutment 330 and its movable abutment 340, such movement being conformable with the extent and direction of the radial adjustment of said movable abutment 340 and being efiected by its pin 353 in conjunction with the corresponding guide slots.325 and 355. This is accomplished by disposing the guide slots 325 and 355 in such relation to the reduced end portions 342 of the movable abutments 340 and in such relation to each other that together with the pins 353 they function to product the desired movement and positioning of the links 350 relative to the movable abutments 340 Each that in all positions of said link 35!! the track surface on or near the end of said link 350 is kept insmooth vane-transferring relation with the overlapping track surface on said movable abutment at the point of lysine transfer. In other words, each guide slot 355 may be said to be positioned along the line generated by movement of the pin 353 when the vane contacting surface of the link 35!! is maintained in vane-transferring relation with thevane-contacting surface on its corresponding movable abutment 343 at the extensible'connection there-between and when said link 3511 and pin, 353 are moved progressively and' conformably toward the pumping arc M as said movable abutment 340 is adjusted from its zero stroke positionto its full stroke position, with the end of said link 350 adjacent the fixed abutment 333 being guided by the pin 55 in the slots 35. A line so generated has,'theoretically, a slight curvature but this curvature is so small that in practice it often maybe neglected and the guide slot 355 may be straight-as in this embodiment. In one aspect, therefore, the function of each guide slot 355 may be said tolbe to permit movement of the link 350 in its extensible connection with the movable abutmentalil, to position, the track surface on the end of the link in vane -transferring relation with the over-lapping track surface of said abutment and, through the pin 353, to'impart movement to the link conformably with inward-or outward adjustment of said movable abutment 340. f

The guide slots 325'are adapted to cause each pin 353 to move progressively and conformably in its guide slot 355 toward the pumping arc 4| as the corresponding movable abutment 340 is moved toward its full stroke position, and vice versa. The guide slots 325 may thus be said to be positioned on the lines generated by the pins 353 when said pin 353, its link 350 and its movable abutment 340 are moved in the manner above stated.

necessary to introduce means tending to hold the vanes II radially outward in contact with the vane track, particularly if the motor is to be operated at low speeds.

It will be understood that the foregoing are merely exemplifying disclosures and that changes, some of which have been indicated,

may be made without departing from applicants In practice the guide slots 325 may be conveniently located by determining the positions of the pin 353 at the positions of the link 353 corresponding to the full stroke and zero stroke positions of its movable abutment 340 and by then connecting the points thus located with a slot having a sliding 'flt with said pm 353. The approximate relation of the guide slots 325 and 355 relative to each other and to the other parts will be understood from the enlarged fragmentary views of Figs. 21 and 22.

With the arrangement of Figs. 13-22, there-' fore, each pin 353 is moved both in its guide slot 355 and its guide slots 325 upon inward or out: ward movement of its movable abutment 340, and it will be observed that said pin 353 can occupy only one position for any given position of its movable abutment. The link 350 through its connection with the pin 353 is thus moved relative to the movable abutment 340 at the extensible connection there-between, its movement being conformable with the movement of said abutment, and said link 35!) is also moved relative to its flxed abutment 335 at the extensible connection between them, the link also'being "rocked" outward as the circumferential length of the trackway is decreased upon inward movement of its movable abutment; two motions or components of motion are thus simultaneously imparted to'the link 350. The movement of the link relative to the fixed abutment 33!! exceeds the radial movement of the abutment 340 invention which. is defined in the appended claims. For example considerable latitude is permissible inthe contour of the track surface on the several vane track elements, and this also is true of the straightening, rounding-off or other forms of easement of the track surfaces at the extensible connections between the track elements. Also, certain individual features of the vane track elements of one embodiment may be employed with other features shown in other 'embodimentsyfor example, the arrangement of the extensible connection at the fixed abutment of the embodiment of Figs. 18-22 may be used with the movable abutment and arrangement of pivotal mounting and overlapping track surfaces therefor shown in the embodiment of Figs.

l2 l4,etc.

In all embodiments, the constructions and arrangements are relatively simple, are capable of large scale production with assured interchangeability of parts and will provide dependable operation of the device. In all embodiments each interconnecting track member has an extensible connection with its adjacent fixed abutment, thereby making possible the use of contours of the vane track which the vanes can follow under the influence of centrifugal force alone, as earlier stated, and which provide improved operation of the pump or motor even and also exceeds the change in, circumferential tions of the movable abutments may be observed in Fig. 18, the left hand half of which shows the abutment 340 in its full stroke position andthe right hand half of which shows the abutment 340 in its zero stroke position.

While the present invention has been described as a pump it is also suitable for use as other types of fluid pressure device, such, for example,

as a fluid motor and it will function as a fluid motor if supplied with pressure fluid for its operation but the cycle of operation will, of course,

be reversed. When employed as a motor it is for moving the vanes radiallyoutward as they pass through the inlet areas. All embodiments also provide a pivotal mounting for each link at the end thereof adjacent its corresponding movable abutment, and in several of the embodiments this pivotal mounting is movable with respect to both the fixed and movable abutments.

which are connected by the link, with outward rocking of the link to provide improved alinement of its track surface with the track surface on the adjacent fixed abutment at the point of vane transfer.

. I claim:

1. In a rotary fluid pressure device of variable capacity, a rotor, a plurality of vanes movable inwardly and outwardly of the rotor, a trackway for the vanes comprising a stationary track element, atrack element movable to vary simultaneously the capacity of the device and the length of the trackway and a link member arranged to connectsaid track elements in all positions of said movable track element, said link member having a pivotal mounting disposed near the end thereof adjacent the movable track element and having an extensible connection with said stationary track element, the entire vanecontacting surface of said link member being of fixed contour, and means for moving said movable track element.

2. ma rotary fluid pressure device of variable capacity, a rotor, a plurality of vanes movable inwardly and outwardly of the rotor, a trackway for the vanes comprising a stationary track element, a track element movable to vary simultaneously the capacity of the device and the length of the trackway and a-link member arranged to connect sa d track elements in all po- 

